Clutch unit

ABSTRACT

A clutch unit includes a lever-side clutch portion for controlling transmission and interruption of rotational torque to an output side through lever operation, and a brake-side clutch portion for transmitting torque input from the lever-side clutch portion to the output side and for interrupting torque reversely input from the output side. The lever-side clutch portion has an outer centering spring provided between a lever-side outer ring to be rotated through the lever operation and a cover restricted in rotation, for accumulating an elastic force obtained by torque input from the lever-side outer ring and for restoring the lever-side outer ring to a neutral state with the accumulated elastic force through releasing of the torque input from the lever-side outer ring.

TECHNICAL FIELD

The present invention relates to a clutch unit having a lever-side clutch portion for transmitting rotational torque from an input side to an output side thereof and a brake-side clutch portion for transmitting rotational torque from the input side to the output side and interrupting torque reversely input from the output side.

BACKGROUND ART

In general, in a clutch unit using engagement elements such as cylindrical rollers or balls, a clutch portion is arranged between an input-side member and an output-side member. Further, in the clutch portion, the engagement elements such as cylindrical rollers or balls are engaged and disengaged with respect to wedge gaps formed between the input-side member and the output-side member, thereby controlling transmission and interruption of the input torque.

The applicant of the present invention has previously proposed a clutch unit incorporated into, for example, an automobile seat-lifter section which vertically adjusts a seat through lever operation. This clutch unit is provided with a lever-side clutch portion for transmitting rotational torque from the input side to the output side and a brake-side clutch portion for transmitting rotational torque from the input side to the output side and interrupting torque reversely input from the output side (see, for example, Patent Literature 1).

FIG. 40 is a longitudinal sectional view of an overall structure of the conventional clutch unit disclosed in Patent Literature 1, FIG. 41 is a sectional view taken along the line D-D of FIG. 40, and FIG. 42 is a sectional view taken along the line E-E of FIG. 40.

As illustrated in FIGS. 40 and 41, a lever-side clutch portion 111 mainly includes a lever-side outer ring 114 serving as an input-side member to which torque is input through lever operation, an inner ring 115 serving as a coupling member for transmitting the torque from the lever-side outer ring 114 to a brake-side clutch portion 112, a plurality of cylindrical rollers 116 serving as engagement elements for controlling transmission and interruption of the torque input from the lever-side outer ring 114 through engagement and disengagement between the lever-side outer ring 114 and the inner ring 115, a retainer 117 for retaining the cylindrical rollers 116 at predetermined circumferential intervals, an inner centering spring 118 serving as a first elastic member which is provided between a brake-side outer ring 123 serving as a stationary-side member restricted in rotation and the retainer 117, for accumulating an elastic force obtained by the torque input from the lever-side outer ring 114 and restoring the retainer 117 to a neutral state with the accumulated elastic force through releasing of the input torque, and an outer centering spring 119 serving as a second elastic member which is provided between the lever-side outer ring 114 and the brake-side outer ring 123, for accumulating an elastic force obtained by the torque input from the lever-side outer ring 114 and restoring the lever-side outer ring 114 to the neutral state with the accumulated elastic force through releasing of the input torque.

Note that, in the figures, reference numeral 113 represents a lever-side side plate fixed to the lever-side outer ring 114 by swaging and constituting the input-side member together with the lever-side outer ring 114, and reference numeral 131 represents a washer mounted to an output shaft 122 through the intermediation of a wave washer 130.

Meanwhile, as illustrated in FIGS. 40 and 42, the brake-side clutch portion 112 mainly includes the brake-side outer ring 123 serving as a stationary-side member restricted in rotation, the inner ring 115 serving as a coupling member to which torque from the lever-side clutch portion 111 is input, and a plurality of pairs of cylindrical rollers 127 serving as engagement elements arranged in wedge gaps 126 between the brake-side outer ring 123 and the output shaft 122, for controlling transmission of torque input from the inner ring 115 and interruption of torque reversely input from the output shaft 122 through engagement and disengagement between the brake-side outer ring 123 and the output shaft 122.

Note that, there is provided a larger diameter portion 115 c extending from an axial end portion of the inner ring 115 in a radially outer direction and bending in an axial direction. In order to cause the larger diameter portion 115 c to function as a retainer for retaining the cylindrical rollers 127 at predetermined circumferential intervals, pockets 115 e for accomodating the cylindrical rollers 127 and plate springs 128 are equiangularly formed. In the figures, reference numerals 124 and 125 respectively represent a cover and a brake-side side plate constituting the stationary-side member together with the brake-side outer ring 123, and the brake-side outer ring 123 and the cover 124 are integrally fixed to each other with the brake-side side plate 125 by swaging. Reference numeral 128 represents a plate spring of, for example, an N-shaped sectional configuration arranged between the cylindrical rollers 127 of each pair, and reference numeral 129 represents a friction ring serving as a braking member mounted to the brake-side side plate 125.

CITATION LIST

[PTL1] JP 2009-210114 A

SUMMARY OF INVENTION Technical Problems

By the way, the conventional clutch unit disclosed in Patent Literature 1 has the following structure. Specifically, the stationary-side member includes the brake-side outer ring 123, the cover 124, and the brake-side side plate 125, and the brake-side outer ring 123 and the cover 124 are integrally fixed to each other with the brake-side side plate 125 by swaging. The conventional clutch unit also has the following structure. Specifically, when the lever-side outer ring 114 is rotated through lever operation, the outer centering spring 119 accumulates an elastic force obtained by torque input from the lever-side outer ring 114, and restores the lever-side outer ring 114 to a neutral state with the accummulated elastic force through releasing of the input torque. The outer centering spring 119 is provided between the lever-side outer ring 114 and the cover 124 constituting the stationary-side member together with the brake-side outer ring 123. The outer centering spring 119 is held in abutment on the cover 124.

In a case of the clutch unit having the above-mentioned structure, when the lever-side outer ring 114 is rotated through lever operation, the outer centering spring 119 accumulates an elastic force obtained by the torque input from the lever-side outer ring 114 and then increases in diameter. Then, at the time of lever operation of restoring a lever from a full stroke to a neutral position, the outer centering spring 119, which slides on the cover 124, may climb onto an inclined portion 124 g of the cover 124 (see FIG. 40) and thus come into contact with the opposing lever-side outer ring 114. When the outer centering spring 119 climbs in this manner by sliding, the outer centering spring 119 comes into contact with the lever-side outer ring 114, with the result that slight noises may occur.

Further, as illustrated in FIG. 43, the above-mentioned outer centering spring 119 is a C-shaped and band-like plate spring which includes a pair of lock portions 119 a formed by bending both ends thereof to a radially outer side. One of the lock portions 119 a and the other of the lock portions 119 a are formed in such a manner that one slit is formed in a center region of each end of the outer centering spring 119 in a peripheral direction and one of both side parts of the slit is bent to the radially outer side. Here, one of the lock portions 119 a is formed by bending the side part on one side in a band-plate width direction, and the other of the lock portions 119 a is formed by bending the side part on the other side in the band-plate width direction. Accordingly, at the time of application of input torque, such a moment force as to pivot the other of the lock portions 119 a about a fulcrum set on the one of the lock portions 119 a is more likely to be generated. As a result, a behavior of the outer centering spring 119 is not stabilized, which may cause occurrence of slight noises.

Therefore, it is an object of the present invention to provide a clutch unit capable of forestalling occurrence of noises caused at the time of lever operation by contact of the outer centering spring with the lever-side outer ring and by an unstable behavior of the outer centering spring.

Solution to Problems

A clutch unit according to the present invention comprises: a lever-side clutch portion provided on an input side, for controlling transmission and interruption of rotational torque to an output side through lever operation; and a brake-side clutch portion provided on the output side, for transmitting torque input from the lever-side clutch portion to the output side and for interrupting torque reversely input from the output side.

The lever-side clutch portion according to the present invention comprises: an input-side member to be rotated through the lever operation; and an elastic member provided between a stationary-side member restricted in rotation and the input-side member, for accumulating an elastic force obtained by torque input from the input-side member and for restoring the input-side member to a neutral state with the accumulated elastic force through releasing of the torque input from the input-side member. The stationary-side member comprises an inclined portion which abuts on the elastic member and swells to the elastic member side. The inclined portion is formed into a shape for controlling an amount of axial movement of the elastic member when the elastic member is restored to an initial state through the releasing of the torque input from the input-side member. Here, it is desired that the shape for controlling the amount of axial movement of the elastic member when the elastic member is restored to the initial state through the releasing of the torque input from the input-side member be formed on a rounded corner surface situated at an outermost diameter of the inclined portion or on an inclined surface extending radially inward from the outermost diameter of the inclined portion.

According to the present invention, the inclined portion is formed into the shape for controlling the amount of axial movement of the elastic member when the elastic member is restored to the initial state through releasing of the torque input from the input-side member. Thus, at the time of lever operation of restoring a lever from a full stroke to a neutral position, it is possible to prevent the elastic member, which slides on the stationary-side member, from climbing onto the inclined portion of the stationary-side member, and to avoid contact of the elastic member with the input-side member. Accordingly, it is possible to prevent occurrence of noises.

The lever-side clutch portion according to the present invention comprises: an input-side member to be rotated through the lever operation; and an elastic member provided between a stationary-side member restricted in rotation and the input-side member, for accumulating an elastic force obtained by torque input from the input-side member and for restoring the input-side member to a neutral state with the accumulated elastic force through releasing of the torque input from the input-side member. The elastic member comprises a C-shaped and band-like plate spring which comprises a pair of lock portions formed by bending both ends thereof to a radially outer side. One of the pair of lock portions and another of the pair of lock portions are formed at positions that are identical in a band-plate width direction. Here, it is desired that the one of the pair of lock portions and the another of the pair of lock portions be formed at center positions in the band-plate width direction or at both side positions in the band-plate width direction.

According to the present invention, the elastic member comprises the C-shaped and band-like plate spring which comprises the pair of lock portions formed by bending both the ends thereof to the radially outer side, and one of the pair of lock portions and another of the pair of lock portions are formed at positions that are identical in the band-plate width direction. Thus, each end of the elastic member is shaped to be symmetric with respect to a center line in a band-plate peripheral direction, and hence it is possible to prevent a moment force generated at the time of application of input torque. Accordingly, a behavior of the elastic member is stabilized, which can prevent occurrence of noises.

The brake-side clutch portion according to the present invention comprises: an output-side member from which torque is output; a stationary-side member restricted in rotation; a coupling member to which the torque is input from the lever-side clutch portion; and a plurality of pairs of engagement elements accommodated in pockets of the coupling member, for controlling transmission of the torque input from the coupling member and interruption of torque reversely input from the output-side member through engagement with and disengagement from wedge gaps formed between the stationary-side member and the output-side member. Any one of width dimensions of the pockets and outer diameter dimensions of the plurality of pairs of engagement elements are set different from one another.

According to the present invention, the width dimensions of the pockets are set different from one another or the outer diameter dimensions of the plurality of pairs of engagement elements are set different from one another. Thus, when the engagement elements are disengaged from the wedge gaps so as to release a locked state of the output-side member, not all the engagement elements are disengaged from the wedge gaps at the same time, but all the engagement elements are disengaged from the wedge gaps in a step-by-step manner. With this operation, even in a case where high load is applied to the output-side member, when the locked state of the output-side member is released, it is possible to avoid concentration of contact pressure, which is generated between the engagement elements due to high load applied to the output-side member, on the engagement element disengaged from the wedge gap last. Accordingly, it is possible to suppress concentration of the contact pressure generated between the engagement elements, and to prevent occurrence of noises at the moment at which the engagement elements are flipped.

According to the present invention, as means for making a difference among the width dimensions of the pockets, the following structure is desired: pockets having small widths and pockets having large widths are arranged alternately in a peripheral direction. With this structure, when the locked state of the output-side member is released, the engagement elements accommodated in the pockets having small widths are disengaged from the wedge gaps prior to the engagement elements accommodated in the pockets having large widths. Thus, all the engagement elements can be disengaged from the wedge gaps substantially one side at a time in a step-by-step and balanced manner, and concentration of the contact pressure generated between the engagement elements is suppressed easily.

According to the present invention, as means for making a difference among the outer diameter dimensions of the plurality of pairs of engagement elements, the following structure is desired: engagement elements having small diameters and engagement elements having large diameters are arranged alternately in a peripheral direction. With this structure, when the locked state of the output-side member is released, the engagement elements having small diameters are disengaged from the wedge gaps prior to the engagement elements having large diameters. Thus, all the engagement elements can be disengaged from the wedge gaps substantially one side at a time in a step-by-step and balanced manner, and concentration of the contact pressure generated between the engagement elements is suppressed easily.

In a case where the coupling member according to the present invention comprises seven or more pockets, it is desired that the seven or more pockets comprise three pockets having large widths and four or more pockets having small widths. With this structure, when the locked state of the output-side member is released, the engagement elements accommodated in the four or more pockets having small widths are disengaged from the wedge gaps, and then the engagement elements accommodated in the minimum necessary three remaining pockets having large widths are disengaged from the wedge gaps. As a result, concentration of the contact pressure generated between the engagement elements is suppressed easily.

In a case where the coupling member according to the present invention comprises seven or more pockets, it is desired that the seven or more pockets accommodate three pairs of engagement elements having large diameters and four or more pairs of engagement elements having small diameters. With this structure, when the locked state of the output-side member is released, the four or more pairs of engagement elements are disengaged from the wedge gaps, and then the minimum necessary three remaining pairs of engagement elements are disengaged from the wedge gaps. As a result, concentration of the contact pressure generated between the engagement elements is suppressed easily.

The brake-side clutch portion according to the present invention comprises: an output-side member from which torque is output; a stationary-side member restricted in rotation; a plurality of pairs of engagement elements arranged in wedge gaps between the stationary-side member and the output-side member, for controlling transmission of the torque input from the lever-side clutch portion and interruption of the torque reversely input from the output side through engagement and disengagement between the stationary-side member and the output-side member; and an elastomer member inserted between the engagement elements of each pair, for imparting a repulsive force to the engagement elements of each pair.

According to the present invention, the elastomer member, which is inserted between the engagement elements of each pair, for imparting the repulsive force to the engagement elements of each pair, can easily increase load applied to the engagement elements. Accordingly, even in a case where high load is applied to the output-side member, when the locked state of the output-side member is released, it is possible to forestall the situation that the elastomer member is to flip the engagement elements, and it is possible to inhibit occurrence of noises.

It is desired that the elastomer member according to the present invention have an outside dimension larger than a gap between the engagement elements of each pair, and be inserted in an elastically deformed state between the engagement elements of each pair. With this structure, an elastic restoring force of the elastomer member acts as a repulsive force to be imparted to the engagement elements, and hence the repulsive force is easily imparted to the engagement elements.

It is desired that the elastomer member according to the present invention have a columnar shape or a quadrangular prism shape, and have an axial dimension equal to or smaller than axial dimensions of the engagement elements of each pair. With this structure, owing to such a simple shape, a function of the elastomer member can be exerted. When the elastomer member has the axial dimension equal to or smaller than the axial dimensions of the engagement elements of each pair, the function of the elastomer member can be exerted reliably, which is effective.

It is desired that the elastomer member according to the present invention be made of any one of a thermosetting elastomer and an elastically deformable resin material. This selection of any one of the thermosetting elastomer and the elastically deformable resin material enables easy manufacture of the elastomer member, which is effective.

In the clutch unit according to the present invention, the lever-side clutch portion and the brake-side clutch portion are incorporated in an automobile seat-lifter section. Thus, the clutch unit is suited for use in an automobile. In this case, the clutch unit has a configuration in which the input-side member is connected to an operation lever and the output-side member is coupled to a link mechanism of the automobile seat-lifter section.

Advantageous Effects of Invention

According to the present invention, the inclined portion is formed into the shape for controlling the amount of axial movement of the elastic member when the elastic member is restored to the initial state through releasing of the torque input from the input-side member. Thus, at the time of lever operation of restoring a lever from a full stroke to a neutral position, it is possible to prevent the elastic member, which slides on the stationary-side member, from climbing onto the inclined portion of the stationary-side member, and to avoid contact of the elastic member with the input-side member. Accordingly, it is possible to prevent occurrence of noises.

Further, the elastic member comprises the C-shaped and band-like plate spring which comprises the pair of lock portions formed by bending both the ends thereof to the radially outer side, and one of the pair of lock portions and another of the pair of lock portions are formed at positions that are identical in the band-plate width direction. Thus, each end of the elastic member is formed into a symmetric shape, and hence it is possible to prevent such a moment force as to pivot the another of the pair of lock portions about a fulcrum set on the one of the pair of lock portions at the time of application of input torque. Accordingly, a behavior of the elastic member is stabilized, which can prevent occurrence of noises.

As a result, it is possible to provide a clutch unit with high reliability. In a case where the clutch unit is incorporated into the automobile seat-lifter section, lever operation of adjusting a seat vertically is performed satisfactorily, and hence comfortable lever operation can be realized for a passenger.

BRIEF DESCRIPTION OF DRAWINGS

[FIG. 1] A longitudinal sectional view of an overall structure of a clutch unit according to an embodiment of the present invention.

[FIG. 2] A right-hand side view of FIG. 1.

[FIG. 3] A left-hand side view of FIG. 1.

[FIG. 4] A sectional view taken along the line A-A of FIG. 1.

[FIG. 5] A sectional view taken along the line B-B of FIG. 1.

[FIG. 6 a] A sectional view of a lever-side side plate.

[FIG. 6 b] A left-hand side view of FIG. 6 a.

[FIG. 7 a] A sectional view illustrating an example of a lever-side outer ring.

[FIG. 7 b] A left-hand side view of FIG. 7 a.

[FIG. 7 c] A right-hand side view of FIG. 7 a.

[FIG. 8 a] A sectional view of an inner ring.

[FIG. 8 b] A left-hand side view of FIG. 8 a.

[FIG. 9] A perspective view of a retainer.

[FIG. 10 a] A sectional view of the retainer.

[FIG. 10 b] A left-hand side view of FIG. 10 a.

[FIG. 10 c] A sectional view of FIG. 10 a.

[FIG. 11] A perspective view of an inner centering spring.

[FIG. 12 a] A perspective view illustrating an example of an outer centering spring.

[FIG. 12 b] A perspective view illustrating another example of the outer centering spring.

[FIG. 13 a] A perspective view of an output shaft seen from one side.

[FIG. 13 b] A perspective view of the output shaft seen from another side.

[FIG. 14 a] A sectional view of the output shaft.

[FIG. 14 b] A left-hand side view of FIG. 14 a.

[FIG. 14 c] A right-hand side view of FIG. 14 a.

[FIG. 15 a] A sectional view of a brake-side outer ring.

[FIG. 15 b] A left-hand side view of FIG. 15 a.

[FIG. 16 a] A sectional view of a cover.

[FIG. 16 b] A right-hand side view of FIG. 16 a.

[FIG. 17 a] A sectional view of a brake-side side plate.

[FIG. 17 b] A right-hand side view of FIG. 17 a.

[FIG. 18 a] A front view of a friction ring.

[FIG. 18 b] A left-hand side view of FIG. 18 a.

[FIG. 18 c] A right-hand side view of FIG. 18 a.

[FIG. 19 a] A perspective view illustrating a state before the brake-side outer ring is assembled to the brake-side side plate.

[FIG. 19 b] A perspective view illustrating a state after the brake-side outer ring is assembled to the brake-side side plate.

[FIG. 20] A perspective view illustrating a state in which the brake-side outer ring and the cover are assembled to the brake-side side plate.

[FIG. 21] A perspective view illustrating a state in which the brake-side side plate, the brake-side outer ring, and the cover are integrated with one another by swaging.

[FIG. 22] A sectional view taken along the line C-C of FIG. 1.

[FIG. 23 a] A perspective view illustrating a state before the retainer is assembled to the brake-side side plate, the brake-side outer ring, the cover, and the inner centering spring.

[FIG. 23 b] A perspective view illustrating a state after the retainer is assembled to the brake-side side plate, the brake-side outer ring, the cover, and the inner centering spring.

[FIG. 24] A longitudinal sectional view illustrating an overall structure of a clutch unit according to another embodiment of the present invention.

[FIG. 25] An enlarged main part sectional view illustrating a state in which cylindrical rollers are flipped and thus a plate spring buckles when a locked state of the output shaft is released.

[FIG. 26] A sectional view illustrating a brake-side clutch portion according to another embodiment of the present invention, in which width dimensions of pockets are set different.

[FIG. 27] An enlarged main part sectional view illustrating a state in which, under the state illustrated in FIG. 26, an inner ring presses cylindrical rollers accommodated in a pocket having a small width and thus the cylindrical rollers are disengaged from a wedge gap.

[FIG. 28] An enlarged main part sectional view illustrating a state in which, under the state illustrated in FIG. 27, the inner ring presses cylindrical rollers accommodated in a pocket having a large width and thus the cylindrical rollers are disengaged from a wedge gap.

[FIG. 29] A sectional view illustrating a brake-side clutch portion according to still another embodiment of the present invention, in which outer diameter dimensions of cylindrical rollers are set different.

[FIG. 30] An enlarged main part sectional view illustrating a state in which, under the state illustrated in FIG. 29, the inner ring presses cylindrical rollers having small diameters and thus the cylindrical rollers are disengaged from a wedge gap.

[FIG. 31] An enlarged main part sectional view illustrating a state in which, under the state illustrated in FIG. 30, the inner ring presses cylindrical rollers having large diameters and thus the cylindrical rollers are disengaged from a wedge gap.

[FIG. 32] A sectional view illustrating a brake-side clutch portion according to still another embodiment of the present invention, in which width dimensions of pockets are set different in a case of comprising seven pockets.

[FIG. 33] A sectional view illustrating a brake-side clutch portion according to still another embodiment of the present invention, in which outer diameter dimensions of cylindrical rollers are set different in a case of comprising seven pockets.

[FIG. 34] A sectional view illustrating a brake-side clutch portion according to still another embodiment of the present invention, in which an elastomer member is inserted between cylindrical rollers of each pair.

[FIG. 35] An enlarged main part sectional view of FIG. 34, for illustrating an embodiment in which an elastomer member having a columnar shape is applied.

[FIG. 36] A sectional view illustrating a state in which, under the state illustrated in FIG. 35, the inner ring presses cylindrical rollers and thus the cylindrical rollers are disengaged from a wedge gap.

[FIG. 37] A sectional view illustrating still another embodiment in which an elastomer member having a quadrangular prism shape is applied.

[FIG. 38] A conceptual view illustrating a seat of an automobile.

[FIG. 39 a] A conceptual view illustrating a structural example of a seat-lifter section.

[FIG. 39 b] An enlarged main part view of FIG. 39 a.

[FIG. 40] A longitudinal sectional view illustrating an overall structure of a conventional clutch unit.

[FIG. 41] A lateral sectional view taken along the line D-D of FIG. 40.

[FIG. 42] A lateral sectional view taken along the line E-E of FIG. 40.

[FIG. 43] A perspective view illustrating an outer centering spring of the conventional clutch unit.

DESCRIPTION OF EMBODIMENTS

FIG. 1 is a longitudinal sectional view of an overall structure of a clutch unit X according to an embodiment of the present invention. FIG. 2 is a right-hand side view of the clutch unit X illustrated in FIG. 1. FIG. 3 is a left-hand side view of the clutch unit X illustrated in FIG. 1. FIG. 4 is a lateral sectional view taken along the line A-A of FIG. 1. FIG. 5 is a lateral sectional view taken along the line B-B of FIG. 1. Further, FIGS. 6 to 18 illustrate main components of the clutch unit X. FIGS. 19 to 23 illustrate assembled states of the main components of the clutch unit X.

The clutch unit X is incorporated into an automobile seat-lifter section (see FIGS. 38, 39 a, and 39 b) for adjusting a height of a seat through lever operation or the like. As illustrated in FIGS. 1 to 5, the clutch unit X comprises a unit of a lever-side clutch portion 11 provided on an input side and a brake-side clutch portion 12 which is provided on an output side and which has a function of interrupting reverse input.

As illustrated in FIGS. 1, 2, and 4, the lever-side clutch portion 11 comprises a lever-side side plate 13 and a lever-side outer ring 14 each serving as an input-side member to which an operation lever (not shown) or the like is connected, an inner ring 15 serving as a coupling member which transmits torque from the lever-side outer ring 14 to the brake-side clutch portion 12, a plurality of cylindrical rollers 16 arranged as an example of engagement elements in wedge gaps 20 formed between an outer peripheral surface 15 a of the inner ring 15 and an inner peripheral surface 14 a of the lever-side outer ring 14, a retainer 17 for retaining the cylindrical rollers 16 equiangularly, an inner centering spring 18 as a first elastic member for restoring the retainer 17 to a neutral state, and an outer centering spring 19 as a second elastic member for restoring the lever-side outer ring 14 to a neutral state. Note that, components are prevented from being detached by press-fitting a washer 31 onto an end portion of an output shaft 22 described later through intermediation of a wave washer 30 (see FIG. 1).

As illustrated in FIGS. 1, 3, and 5, the so-called lock type brake-side clutch portion 12 which has a function of interrupting reverse input mainly comprises the inner ring 15 serving as a coupling member to which the torque from the lever-side clutch portion 11 is input, the output shaft 22 serving as an output-side member, a brake-side outer ring 23, a cover 24, and a brake-side side plate 25 each serving as a stationary-side member restricted in rotation, a plurality of pairs of cylindrical rollers 27 arranged as engagement elements in wedge gaps 26 between the brake-side outer ring 23 and the output shaft 22, for controlling transmission of the torque input from the inner ring 15 and interruption of the torque reversely input from the output shaft 22 through engagement and disengagement between both the members, and plate springs 28 of, for example, an N-shaped sectional configuration, each inserted between the cylindrical rollers 27 of each pair and serving as elastic members for imparting repulsive force to the cylindrical rollers 27. Note that, protrusions 22 f are provided to the output shaft 22 and inserted into holes 15 d with clearances, which are provided to the inner ring 15 (see FIG. 1).

Next, detailed description is made of main components of the lever-side clutch portion 11 and the brake-side clutch portion 12 which are provided in the clutch unit X.

FIGS. 6 a and 6 b illustrate the lever-side side plate 13 of the lever-side clutch portion 11. In the lever-side side plate 13, a hole 13 a into which the output shaft 22 and the inner ring 15 are inserted is formed in a center portion thereof, and a plurality of (five, for example) claw portions 13 b are provided in a protruding manner on an outer peripheral portion thereof. Those claw portions 13 b are bent and molded in an axial direction so as to have bisected distal ends. Then, the claw portions 13 b are inserted into cutout recessed portions 14 e (see FIG. 7 c) of the lever-side outer ring 14, which are described later. Lastly, the distance between each of the bisected distal ends is increased outward. In this manner, the lever-side side plate 13 is fixed to the lever-side outer ring 14 by swaging. Note that, in the figures, a plurality of (four, for example) holes for mounting the operation lever (not shown) for adjusting a height of a seat to the lever-side side plate 13 are represented by reference symbol 13 c.

FIGS. 7 a to 7 c illustrate the lever-side outer ring 14. The lever-side outer ring 14 is obtained by molding a plate-like material into a cup-shape through press working, and comprises a hole 14 b formed in a center portion 14 c, through which the output shaft 22 and the inner ring 15 are inserted. On an inner periphery of a cylindrical portion 14 d extending from the center portion 14 c in the axial direction, a plurality of cam surfaces 14 a are equiangularly formed (see FIG. 4).

On an outer peripheral portion of the lever-side outer ring 14, a plurality of (three, for example) claw portions 14 f and 14 g are provided in a protruding manner and bent and molded in the axial direction. Of those claw portions 14 f and 14 g, the one claw portion 14 f is locked by being inserted and arranged between two lock portions 19 a (see FIGS. 12 a and 12 b) of the outer centering spring 19 described later. In a state of being in contact with an end surface of the brake-side outer ring 23 described later, the other two claw portions 14 g slide on the end surface of the brake-side outer ring 23 in accordance with rotation of the lever-side outer ring 14, and move between a pair of lock portions 24 e and 24 f (see FIG. 16 b) as rotation stoppers provided on an outer periphery of the cover 24 so as to be abuttable on the lock portion 24 e and 24 f, respectively, at moving ends in a rotational direction. In this manner, an operating angle of the operation lever is restricted.

The plurality of (five in the figure) cutout recessed portions 14 e into which the claw portions 13 b (see FIGS. 6 a and 6 b) of the lever-side side plate 13 are inserted are formed on an outer periphery of the lever-side outer ring 14. By swaging the claw portions 13 b of the lever-side side plate 13, which are inserted into the cutout recessed portions 14 e, the lever-side side plate 13 and the lever-side outer ring 14 are connected to each other. The lever-side outer ring 14 and the lever-side side plate 13 fixed by swaging to the lever-side outer ring 14 constitute the input-side member of the lever-side clutch portion 11.

FIGS. 8 a and 8 b illustrate the inner ring 15. The inner ring 15 is provided with the outer peripheral surface 15 a formed on an outer diameter of a cylindrical portion 15 b into which the output shaft 22 is inserted, the wedge gaps 20 (see FIG. 4) being formed between the outer peripheral surface 15 a and the cam surfaces 14 a of the lever-side outer ring 14. Further, a larger diameter portion 15 c extending from an end portion of the cylindrical portion 15 b in a radially outer direction and bending in the axial direction is integrally formed. In order to cause the larger diameter portion 15 c to function as a retainer for the brake-side clutch portion 12, pockets 15 e for accommodating the cylindrical rollers 27 and the plate springs 28 are equiangularly formed in the larger diameter portion 15 c. Note that, in the figures, holes into which the protrusions 22 f of the output shaft 22 (see FIG. 1) are inserted with clearances are represented by a reference symbol 15 d.

FIGS. 9, and 10 a to 10 c illustrate the retainer 17 made of a resin. The retainer 17 is a cylindrical member in which a plurality of pockets 17 a for accommodating the cylindrical rollers 16 are equiangularly formed. Two cutout recessed portions 17 b are formed in one end portion of the retainer 17, and lock portions 18 a of the above-mentioned inner centering spring 18 are locked to two adjacent end surfaces 17 c of the respective cutout recessed portions 17 b (see FIG. 22).

FIG. 11 illustrates the inner centering spring 18. The inner centering spring 18 is a spring having a circular C-shape in cross-section and comprising a pair of the lock portions 18 a bent to a radially inner side, and is situated on the radially inner side of the outer centering spring 19 (see FIG. 22). The inner centering spring 18 is arranged between the retainer 17 and the cover 24 serving as a stationary-side member of the brake-side clutch portion 12. In addition, both the lock portions 18 a are locked to the two end surfaces 17 c (see FIGS. 9 and 10 b) of the retainer 17 and locked to a claw portion 24 b (see FIGS. 16 a and 16 b) provided to the cover 24 (see FIGS. 22, 23 a and 23 b).

At the time of application of torque input from the lever-side outer ring 14 in the inner centering spring 18, one of the lock portions 18 a is engaged with one of the end surfaces 17 c of the retainer 17, and the other of the lock portions 18 a is engaged with the claw portion 24 b of the cover 24. Thus, the inner centering spring 18 is pressed and extended in accordance with rotation of the lever-side outer ring 14 so as to accumulate an elastic force. At the time of releasing the torque input from the lever-side outer ring 14, the retainer 17 is restored to a neutral state with the elastic restoring force.

FIG. 12 a illustrates an example of the outer centering spring 19. The outer centering spring 19 is a C-shaped and band plate-like spring comprising the pair of lock portions 19 a formed by bending both the ends thereof to a radially outer side, and is situated on a radially outer side of the inner centering spring 18 (see FIG. 22). The outer centering spring 19 is arranged between the lever-side outer ring 14 of the lever-side clutch portion 11 and the cover 24 of the brake-side clutch portion 12. Both the lock portions 19 a are locked to the claw portion 14 f (see FIGS. 7 a to 7 c) provided to the lever-side outer ring 14, and also locked to a claw portion 24 d (see FIGS. 16 a and 16 b) provided to the cover 24 (see FIGS. 23 a and 23 b). The lock portions 19 a are arranged while being displaced (by 180°) in a circumferential direction with respect to the lock portions 18 a of the inner centering spring 18 (see FIG. 22).

In the outer centering spring 19, when the torque input from the lever-side side plate 13 is applied through lever operation so as to rotate the lever-side outer ring 14, one of the lock portions 19 a is engaged with the claw portion 14 f of the lever-side outer ring 14, and the other of the lock portions 19 a is engaged with the claw portion 24 d of the cover 24, respectively. Thus, the outer centering spring 19 is pressed and extended in accordance with the rotation of the lever-side outer ring 14 so as to accumulate an elastic force. After the outer center spring 19 is increased in diameter, when the torque input from the lever-side outer ring 14 is released, the lever-side outer ring 14 is restored to a neutral state with the elastic restoring force.

Unlike in the conventional outer centering spring 119 (see FIG. 43), in the outer centering spring 19 illustrated in FIG. 12 a, one of the lock portions 19 a and the other of the lock portions 19 a are formed at center positions that are identical in a band-plate width direction. That is, one of the lock portions 19 a and the other of the lock portions 19 a are formed in such a manner that two slits are formed in each end of the outer centering spring 19 in a peripheral direction and a center part situated between the two slits is bent to a radially outer side. Thus, each end of the outer centering spring 19 is shaped to be symmetric with respect to a center line in a band-plate peripheral direction, and hence it is possible to prevent a moment force generated at the time of application of input torque, i.e., such a force as to pivot the other of the lock portions 19 a about a fulerum set on one of the lock portions 19 a. Accordingly, a behavior of the outer centering spring 19 is stabilized, which can prevent occurrence of noises.

Note that, it is only necessary that each end of the outer centering spring 19 be shaped to be symmetric with respect to the center line in the band-plate peripheral direction, and hence, for example, an outer centering spring 19′ as illustrated in FIG. 12 b may be employed. The outer centering spring 19′ is a C-shaped and band-like plate spring which comprises a pair of lock portions 19 a′ formed by bending each end thereof to the radially outer side. One of the lock portions 19 a′ and the other of the lock portions 19 a′ are formed at both side positions that are identical in the band-plate width direction. That is, one of the lock portions 19 a′ and the other of the lock portions 19 a′ are formed in such a manner that two slits are formed in each end of the outer centering spring 19′ in the peripheral direction and both side parts situated on the outer side of the two slits are bent to the radially outer side. Also in this case, it is possible to prevent a moment force generated at the time of application of input torque, i.e., such a force as to pivot the other of the lock portions 19 a′ about a fulerum set on one of the lock portions 19 a′. Accordingly, a behavior of the outer centering spring 19′ is stabilized, which can prevent occurrence of noises.

FIGS. 13 a and 13 b and FIGS. 14 a to 14 c illustrate the output shaft 22. The output shaft 22 comprises a larger diameter portion 22 d which extends from a shaft portion 22 c to the radially outer side to be increased in diameter, and is integrally formed substantially in an axial center region of the output shaft 22. A pinion gear 41 g to be coupled to a seat-lifter section 41 is coaxially formed on a distal end of the shaft portion 22 c.

A plurality of (six, for example) flat cam surfaces 22 a are equiangularly formed on an outer peripheral surface of the larger diameter portion 22 d, and the two cylindrical rollers 27 and the plate spring 28 are arranged in each wedge gap 26 (see FIG. 5) provided between the cam surfaces 22 a and an inner peripheral surface 23 b of the brake-side outer ring 23. In one end surface of the larger diameter portion 22 d, there is formed an annular recessed portion 22 b in which a friction ring 29 is accommodated and arranged. Further, in the figures, protrusions formed on the other end surface of the larger diameter portion 22 d are represented by reference symbol 22 f, the protrusions being inserted into the holes 15 d of the inner ring 15 with clearances (see FIGS. 1, 8 a, and 8 b).

FIGS. 15 a and 15 b illustrate the brake-side outer ring 23, and FIGS. 16 a and 16 b illustrate the cover 24. FIGS. 17 a and 17 b illustrate the brake-side side plate 25. The brake-side outer ring 23 and the cover 24 described above are integrally fixed to each other with the brake-side side plate 25 by swaging. The brake-side outer ring 23 is formed of a thick plate-like member obtained by punching of a single material with a press, and the cover 24 is molded by pressing of another single material. As illustrated in FIGS. 16 a and 16 b, the cover 24 has an inclined portion 24 g, which swells to the outer centering spring 19 side in a state of abutting on the larger diameter portion 15 c of the inner ring 15 described above (see FIG. 1). Note that, in the figures, holes into which the output shaft 22 is inserted are represented by reference symbols 24 c and 25 b, and holes to which protrusions 29 a of the friction ring 29 described later are fitted are represented by reference symbol 25 c.

The clutch unit X has the following structure. Specifically, the outer centering spring 19 is arranged between the cover 24 and the lever-side outer ring 14, and the outer centering spring 19 abuts on the cover 24 on the radially outer side of the inclined portion 24 g of the cover 24. Here, at the time of lever operation of restoring a lever from a full stroke to a neutral position, the outer centering spring 19, which slides on the cover 24, climbs onto the inclined portion 24 g of the cover 24 and thus comes into contact with the opposing lever-side outer ring 14. As a result, slight noises may occur. Accordingly, the inclined portion 24 g of the cover 24 is formed into a shape for controlling an amount of axial movement of the outer centering spring 19 when the outer centering spring 19 is restored to an initial state by releasing of input torque.

That is, according to the embodiment illustrated in FIG. 1, a curvature radius of a rounded corner surface 24 g ¹ situated at an outermost diameter of the inclined portion 24 g of the cover 24 is set larger than a curvature radius of a rounded corner surface 124 g ₁ situated at an outermost diameter of the inclined portion 124 g of the conventional cover 124 (see FIG. 40). Thus, a swelling height of the inclined portion 24 g is changed gradually with respect to a radial change of the outer centering spring 19 when the outer centering spring 19 climbs onto the inclined portion 24 g of the cover 24 at the time of lever operation of restoring the lever from a full stroke to a neutral position, and thus the amount of axial movement of the outer centering spring 19 can be controlled. As a result, it is possible to prevent the outer centering spring 19 from climbing onto the inclined portion 24 g of the cover 24, and to avoid contact of the outer centering spring 19 with the lever-side outer ring 14. Therefore, it is possible to prevent occurrence of noises.

Further, as another embodiment, as illustrated in FIG. 24, an angle of an inclined surface 24 g ₂ extending radially inward from the outermost diameter of the inclined portion 24 g of the cover 24 may be set smaller than an angle of an inclined surface 124 g ₂ extending radially inward from the outermost diameter of the inclined portion 124 g of the conventional cover 124 (see FIG. 40). Thus, the swelling height of the inclined portion 24 g is changed gradually with respect to the radial change of the outer centering spring 19 when the outer centering spring 19 climbs onto the inclined portion 24 g of the cover 24 at the time of lever operation of restoring the lever from a full stroke to a neutral position, and thus the amount of axial movement of the outer centering spring 19 can be controlled. As a result, it is possible to prevent the outer centering spring 19 from climbing onto the inclined portion 24 g of the cover 24, and to avoid contact of the outer centering spring 19 with the lever-side outer ring 14. Therefore, it is possible to prevent occurrence of noises.

A plurality of (three) cutout recessed portions 23 a are formed on an outer periphery of the brake-side outer ring 23. Correspondingly to the cutout recessed portions 23 a, a plurality of (three) cutout recessed portions 24 a are similarly formed on an outer periphery of the cover 24. As illustrated in FIGS. 19 a and 19 b, claw portions 25 a of the brake-side side plate 25 are inserted into the cutout recessed portions 23 a of the brake-side outer ring 23, respectively. Further, as illustrated in FIG. 20, the claw portions 25 a of the brake-side side plate 25 are inserted into the cutout recessed portions 24 a of the cover 24, respectively.

The claw portions 25 a of the brake-side side plate 25 are inserted into the cutout recessed portions 23 a and 24 a. By swaging the claw portions 25 a of the brake-side side plate 25, the brake-side outer ring 23 and the cover 24 are coupled to each other and integrated with the brake-side side plate 25, to thereby form the stationary-side member. Swaging of the claw portions 25 a of the brake-side side plate 25 is performed by increasing outward the distance between bisected distal end portions 25 a ₁ of each of the claw portions 25 a with use of a swage (not shown) (see FIG. 21).

The wedge gaps 26 are formed between the inner peripheral surface 23 b of the brake-side outer ring 23 and the cam surfaces 22 a of the output shaft 22 (see FIG. 5). The cover 24 is provided with the claw portion 24 b protruding in the axial direction, the claw portion 24 b being arranged between the two lock portions 18 a of the inner centering spring 18 of the lever-side clutch portion 11 (see FIGS. 11, 23 a, and 23 b). The claw portion 24 b of the cover 24 is formed by raising the surface of the cover 24 on the radially outer side of the claw-portion-formation position. The claw portion 24 d protruding in the axial direction is formed on the outer periphery of the cover 24. The claw portion 24 d is arranged between the two lock portions 19 a of the outer centering spring 19 of the lever-side clutch portion 11 (see FIGS. 12 a, 23 a and 23 b).

Two pairs of the lock portions 24 e and 24 f are formed by stepping on the outer periphery of the cover 24 (see FIGS. 23 a and 23 b). In a state in which the cover 24 is held in contact with the end surface of the brake-side outer ring 23, in accordance with rotation of the lever-side outer ring 14, the lock portions 24 e and 24 f are allowed to be brought into abutment, in a rotational direction, on the claw portions 14 g, which slide on the end surface of the brake-side outer ring 23. As a result, the lock portions 24 e and 24 f function as rotation stoppers for restricting an operating angle of the operation lever. In other words, when the lever-side outer ring 14 is rotated through operation of the operation lever, the claw portions 14 g thereof move along the outer periphery of the cover 24 between the lock portions 24 e and 24 f of the cover 24.

On the outer periphery of the brake-side sideplate 25, one flange portion 25 e and two flange portions 25 f are provided as clutch mounting portions with respect to the seat-lifter section (see FIGS. 2 to 4). In distal end portions of those three flange portions 25 e and 25 f, there are formed, by boring, mounting holes 25 g and 25 h for allowing mounting with respect to the seat-lifter section, and there are protrudingly formed, in the axial direction, cylindrical portions 25 i and 25 j in a manner of surrounding the mounting holes 25 g and 25 h.

FIGS. 18 a to 18 c illustrate the friction ring 29 made of a resin. On an end surface of the friction ring 29, the plurality of circular protrusions 29 a are equiangularly formed. By press-fitting and engaging the protrusions 29 a into the holes 25 c of the brake-side side plate 25, the friction ring 29 is fixed to the brake-side side plate 25 (see FIGS. 1 and 3).

In the case of press-fitting of the protrusions 29 a, an engagement state with the holes 25 c can be achieved due to elastic deformation of the protrusions 29 a made of a resin material. By adopting a press-fit engagement structure of the protrusions 29 a and the holes 25 c, it is possible to prevent the friction ring 29 from falling off from the brake-side side plate 25 due to handling during transportation or the like. As a result, it is possible to increase handling properties at the time of assembly.

The friction ring 29 is press-fitted to an inner peripheral surface 22 e of the annular recessed portion 22 b formed in the larger diameter portion 22 d of the output shaft 22 with fastening allowance (see FIGS. 13 a, 14 a and 14 b). Due to a frictional force generated between an outer peripheral surface 29 c of the friction ring 29 and the inner peripheral surface 22 e of the annular recessed portion 22 b of the output shaft 22, rotational resistance is imparted to the output shaft 22.

On the outer peripheral surface 29 c of the friction ring 29, there are equiangularly formed a plurality of recessed groove-like slits 29 b (see FIG. 5). With provision of the slits 29 b as in this case, elasticity may be imparted to the friction ring 29. Thus, a rate of change in sliding torque is not increased with respect to inner diameter tolerance of the output shaft 22 and outer diameter tolerance of the friction ring 29.

In other words, it is possible to reduce a setting range of rotational resistance imparted by the frictional force generated between the outer peripheral surface 29 c of the friction ring 29 and the inner peripheral surface 22 e of the annular recessed portion 22 b of the output shaft 22, and hence to appropriately and easily set the degree of the rotational resistance. Further, the slits 29 b serve as grease pools, and hence it is possible to suppress abrasion of the outer peripheral surface 29 c of the friction ring 29 due to sliding with respect to the inner peripheral surface 22 e of the annular recessed portion 22 b of the output shaft 22.

Description is made on operation of the lever-side clutch portion 11 and the brake-side clutch portion 12 of the clutch unit X structured as described above.

In the lever-side clutch portion 11, when the input torque is applied to the lever-side outer ring 14, the cylindrical rollers 16 are engaged into the wedge gaps 20 between the lever-side outer ring 14 and the inner ring 15. The inner ring 15 is rotated with torque transmitted to the inner ring 15 through the intermediation of the cylindrical rollers 16. Simultaneously, an elastic force is accumulated in both the centering springs 18 and 19 in accordance with the rotation of the lever-side outer ring 14 and the retainer 17. When the input torque is interrupted, the lever-side outer ring 14 and the retainer 17 are restored to a neutral state with the elastic force of both the centering springs 18 and 19. Meanwhile, the inner ring 15 is maintained at the fixed rotational position. Accordingly, the inner ring 15 is rotated in an inching manner with repetitive rotation of the lever-side outer ring 14, in other words, pumping operation of the operation lever.

In the brake-side clutch portion 12, when reverse-input torque is input to the output shaft 22, the plate spring 28 imparts a repulsive force to the cylindrical rollers 27 of each pair, and thus the cylindrical rollers 27 are engaged into the wedge gap 26 between the output shaft 22 and the brake-side outer ring 23 so as to lock the output shaft 22 with respect to the brake-side outer ring 23. Therefore, the torque reversely input from the output shaft 22 is locked by the brake-side clutch portion 12 so as to interrupt back-flow of the torque reversely input to the lever-side clutch portion 11.

Meanwhile, the torque input from the lever-side outer ring 14 is input to the inner ring 15 through the intermediation of the lever-side clutch portion 11. When the inner ring 15 is brought into abutment on the cylindrical rollers 27 and presses the cylindrical rollers 27 against the elastic force of the plate springs 28, the cylindrical rollers 27 are disengaged from the wedge gaps 26 and a locked state of the output shaft 22 is released. As a result, the output shaft 22 is allowed to be rotated. When the inner ring 15 is further rotated, clearances between the holes 15 d of the inner ring 15 and the protrusions 22 f of the output shaft 22 are narrowed, and the inner ring 15 is brought into abutment on the protrusions 22 f of the output shaft 22 in a rotational direction. As a result, the torque input from the inner ring 15 is transmitted to the output shaft 22 through the intermediation of the protrusions 22 f, and the output shaft 22 is rotated.

Here, in a case where high load is applied to the output shaft 22, contact pressure generated between the cylindrical rollers 27 is increased. As a result, when the cylindrical rollers 27 are disengaged from the wedge gap 26 so as to release a locked state of the output shaft 22, as illustrated in FIG. 25, one engaging cylindrical roller (cylindrical roller 27 on the left side of FIG. 25), which is pressed by the larger diameter portion 15 c of the inner ring 15 functioning as the retainer, is flipped toward the other cylindrical roller (cylindrical roller 27 on the right side of FIG. 25), and thus the plate spring 28 may buckle. When the plate spring 28 buckles in this manner, each of the cylindrical rollers 27 cannot be restored to an initial position after releasing the locking. Further, there is a fear in that vibration generated at the moment at which the cylindrical rollers 27 are flipped causes noises.

In the clutch unit according to the above-mentioned embodiment, all the pockets 15 e are set to have the same circumferential width dimensions, the pockets 15 e being formed equiangularly in the larger diameter portion 15 c of the inner ring 15, for accommodating the cylindrical rollers 27 and the plate springs 28. However, as well as the width dimensions of the pockets 15 e, an inner diameter dimension of the brake-side outer ring 23, a roundness of the inner diameter of the brake-side outer ring 23, outer diameter dimensions of the cylindrical rollers 27, and a cam surface dimension of the output shaft 22 vary. Accordingly, when the cylindrical rollers 27 are disengaged from the wedge gaps 26 so as to release the locked state of the output shaft 22, it may be difficult to disengage all the cylindrical rollers 27 from the wedge gaps 26 at the same time.

As described above, in a case where it is difficult to disengage all the cylindrical rollers 27 from the wedge gaps 26 at the same time, when the cylindrical rollers 27 are disengaged from the wedge gaps 26 so as to release the locked state of the output shaft 22, the contact pressure, which is generated between the cylindrical rollers 27 due to high load applied to the output shaft 22, is concentrated on the cylindrical roller 27 that is disengaged from the wedge gap 26 last. As a result, the cylindrical rollers 27 are flipped, and hence the plate springs 28 are more likely to buckle. Accordingly, it is extremely difficult to restore each of the cylindrical rollers 27 to an initial position, and noises are more likely to occur at the moment at which the cylindrical rollers 27 are flipped.

In this context, when the locked state of the output shaft 22 is released, in order to suppress concentration of the contact pressure generated between the cylindrical rollers 27, and to prevent occurrence of noises at the moment at which the cylindrical rollers 27 are flipped, in the clutch unit according to this embodiment, as illustrated in FIG. 26, width dimensions W₁ of pockets 15 e ₁ are set different from width dimensions W₂ of pockets 15 e ₂ (W₁<W₂). That is, the pockets 15 e ₁ having small widths and the pockets 15 e ₂ having large widths are arranged alternately in the peripheral direction. As described above, the pockets 15 e ₁ having small widths and the pockets 15 e ₂ having large widths are arranged alternately in the peripheral direction, and hence when the cylindrical rollers 27 are disengaged from the wedge gaps 26 so as to release the locked state of the output shaft 22, not all the cylindrical rollers 27 are disengaged from the wedge gaps 26 at the same time, but the following operation is provided instead. Specifically, as illustrated in FIG. 27, by being pressed by the larger diameter portion 15 c of the inner ring 15, the cylindrical rollers 27 accommodated in the pocket 15 e ₁ having a small width are disengaged from the wedge gap 26 prior to the cylindrical rollers 27 accommodated in the pocket 15 e ₂ having a large width. Then, as illustrated in FIG. 28, by being pressed by the larger diameter portion 15 c of the inner ring 15, the cylindrical rollers 27 accommodated in the pocket 15 e ₂ having the large width are disengaged from the wedge gap 26. In this way, all the cylindrical rollers 27 are disengaged from the wedge gaps 26 one side at a time in a step-by-step and balanced manner.

Besides setting of the width dimensions W₁ of the pockets 15 e ₁ to be different from the width dimensions W₂ of the pockets 15 e ₂ as in this embodiment, as another embodiment, as illustrated in FIG. 29, outer diameter dimensions D₁ of cylindrical rollers 27 a of each pair may be set different from outer diameter dimensions D₂ of cylindrical rollers 27 b of each pair (D₁<D₂). That is, the cylindrical rollers 27 a having small diameters (outer diameter dimensions D₁) and the cylindrical rollers 27 b having large diameters (outer diameter dimensions D₂) may be arranged alternately in the peripheral direction. As described above, the cylindrical rollers 27 a having small diameters and the cylindrical rollers 27 b having large diameters are arranged alternately in the peripheral direction, and hence the following operation is provided. Specifically, when the locked state of the output shaft 22 is released, as illustrated in FIG. 30, by being pressed by the larger diameter portion 15 c of the inner ring 15, the cylindrical rollers 27 a having small diameters are disengaged from the wedge gap 26 prior to the cylindrical rollers 27 b having large diameters. Then, as illustrated in FIG. 31, by being pressed by the larger diameter portion 15 c of the inner ring 15, the cylindrical rollers 27 b having large diameters are disengaged from the wedge gap 26. In this way, all the cylindrical rollers 27 a and 27 b are disengaged from the wedge gaps 26 one side at a time in a step-by-step and balanced manner.

As described above, the pockets 15 e ₁ having small widths and the pockets 15 e ₂ having large widths are arranged alternately in the peripheral direction, or the cylindrical rollers 27 a having small diameters and the cylindrical rollers 27 b having large diameters are arranged alternately in the peripheral direction, and thus the following operation is provided. Specifically, even in a case where high load is applied to the output shaft 22, when the locked state of the output shaft 22 is released, it is possible to avoid concentration of the contact pressure, which is generated between the cylindrical rollers 27 (27 a, 27 b) due to high load applied to the output shaft 22, on the cylindrical roller 27 (27 a, 27 b) that is disengaged from the wedge gap 26 last. Accordingly, it is possible to suppress concentration of the contact pressure generated between the cylindrical rollers 27 (27 a, 27 b), and to prevent occurrence of noises at the moment at which the cylindrical rollers (27 a, 27 b) are flipped.

Note that, in the above-mentioned embodiments, description is made of a case where six pockets 15 e ₁ and 15 e ₂ (15 e) are provided. In a case where the larger diameter portion 15 c of the inner ring 15 functioning as the retainer comprises seven or more pockets 15 e ₁ and 15 e ₂ (15 e), the following structure is adopted.

In the structure in which the width dimensions W₁ of the pockets 15 e ₁ are set different from the width dimensions W₂ of the pockets 15 e ₂, in a case where eight pockets 15 e ₁ and 15 e ₂ are provided as in an embodiment illustrated in FIG. 32, three pockets 15 e ₂ having large widths and four or more (five in this embodiment) pockets 15 e ₁ having small widths are provided. With this structure, when the locked state of the output shaft 22 is released, the cylindrical rollers 27 accommodated in the four or more (five) pockets 15 e ₁ having small widths are disengaged from the wedge gaps 26, and then the cylindrical rollers 27 accommodated in the minimum necessary three remaining pockets 15 e ₂ having large widths are disengaged from the wedge gaps 26. As a result, concentration of the contact pressure generated between the cylindrical rollers 27 is suppressed easily.

Further, in the structure in which the outer diameter dimensions D₁ of the cylindrical rollers 27 a are set different from the outer diameter dimensions D₂ of the cylindrical rollers 27 b, in a case where eight pockets 15 e are provided as in an embodiment illustrated in FIG. 33, three pairs of cylindrical rollers 27 b having large diameters and four or more pairs (five pairs in this embodiment) of cylindrical rollers 27 a having small diameters are provided. With this structure, when the locked state of the output shaft 22 is released, the four or more pairs (five pairs) of cylindrical rollers 27 a having small diameters are disengaged from the wedge gaps 26, and then the minimum necessary three remaining pairs of cylindrical rollers 27 b having large diameters are disengaged from the wedge gaps 26. As a result, concentration of the contact pressure generated between the cylindrical rollers 27 a, 27 b of each pair is suppressed easily.

In the above-mentioned embodiments, the output shaft 22 is locked by an elastic force of the plate spring 28, and the locked state of the output shaft 22 is released against the elastic force of the plate spring 28. Because of a shape, a plate thickness, and the like of the plate spring 28, spring load of the plate spring 28 has limitations with respect to load applied to the cylindrical rollers 27. Therefore, in a case where load applied to the cylindrical rollers 27 is increased, it is necessary to prepare means other than the plate spring 28.

In this context, when the locked state of the output shaft 22 is released, in order to forestall the situation that the cylindrical rollers 27 are flipped and thus the plate springs 28 may buckle, and to prevent occurrence of noises caused by vibration at the moment at which the cylindrical rollers 27 are flipped, instead of the plate springs 28 used in the above-mentioned embodiments, as illustrated in FIG. 34, an elastomer member 28 a for imparting a repulsive force to the cylindrical rollers 27 of each pair may be inserted between the cylindrical rollers 27 of each pair.

The elastomer member 28 a has an outer diameter dimension larger than a gap between the cylindrical rollers 27 of each pair, and is inserted in an elastically deformed state between the cylindrical rollers 27 (see FIG. 35). That is, as illustrated in FIG. 35, regions of the elastomer member 28 a abutting on the cylindrical rollers 27 are elastically deformed and dented by a pressing force applied from the cylindrical rollers 27. With this, an elastic restoring force of the elastomer member 28 a acts as a repulsive force to be imparted to the cylindrical rollers 27, and hence the repulsive force is easily imparted to the cylindrical rollers 27.

Further, the elastomer member 28 a has a columnar shape and an axial dimension equal to or smaller than axial dimensions of the cylindrical rollers 27. Owing to a simple shape such as the columnar shape, a function of the elastomer member 28 a, i.e., a function of imparting the repulsive force to the cylindrical rollers 27 can be exerted. Further, when the axial dimension of the elastomer member 28 a is set equal to or smaller than the axial dimensions of the cylindrical rollers 27, the elastomer member 28 a can reliably exert the function of imparting the repulsive force to the cylindrical rollers 27 without interfering with other components.

As described above, the output shaft 22 is locked by the elastic force of the elastomer member 28 a, and the locked state of the output shaft 22 is released against the elastic force of the elastomer member 28 a. In this embodiment, compared to the plate spring 28 (see FIG. 5), the elastomer member 28 a inserted between the cylindrical rollers 27 of each pair and having the function of imparting the repulsive force to the cylindrical rollers 27 can easily increase the load applied to the cylindrical rollers 27.

As a result, even in a case where high load is applied to the output shaft 22, when the cylindrical rollers 27 are disengaged from the wedge gaps 26 so as to release the locked state of the output shaft 22, the following operation is provided. Specifically, as illustrated in FIG. 36, owing to the elastomer member 28 a that does not buckle unlike the plate spring 28 (see FIG. 25), one engaging cylindrical roller (cylindrical roller 27 on the left side of FIG. 36) pressed by the inner ring 15 is not flipped toward the other cylindrical roller (cylindrical roller 27 on the right side of FIG. 36), and the elastomer member 28 a can reliably restore each of the cylindrical rollers 27 to an initial position after releasing the locking. Accordingly, it is possible to prevent occurrence of noises caused by vibration at the moment at which the cylindrical rollers 27 are flipped.

Note that, the elastomer member 28 a is made of any one of a thermosetting elastomer and an elastically deformable resin material. This selection of anyone of the thermosetting elastomer and the elastically deformable resin material enables easy manufacture of the elastomer member 28 a. Further, as illustrated in FIG. 37, the elastomer member 28 b may have a quadrangular prism shape, and a sectional shape of the elastomer member may be set arbitrarily.

The clutch unit X provided with the structure as described above in detail is used while being incorporated into, for example, an automobile seat-lifter section. FIG. 38 illustrates a seat 40 installed in a cabin of an automobile. The seat 40 comprises a sitting seat 40 a, a backrest seat 40 b, and the seat-lifter section 41 for adjusting a height H of the sitting seat 40 a. Adjustment of the height H of the sitting seat 40 a is performed with an operation lever 41 a of the seat-lifter section 41.

FIG. 39 a is a conceptual view of a structural example of the seat-lifter section 41. One ends of link members 41 c and 41 d are pivotally mounted to a slide movable member 41 b ₁ of a seat slide adjuster 41 b. The other ends of the link members 41 c and 41 d are pivotally mounted to the sitting seat 40 a. The other end of the link member 41 c is pivotally mounted to a sector gear 41 f through intermediation of a link member 41 e. The sector gear 41 f is pivotally mounted to the sitting seat 40 a, and pivotable about a fulcrum 41 f ₁. The other end of the link member 41 d is pivotally mounted to the sitting seat 40 a.

The clutch unit X described above in this embodiment is fixed to an appropriate position of the sitting seat 40 a. Fixation of the clutch unit X to the sitting seat 40 a is fixation by swaging to a seat frame (not shown) of the sitting seat 40 a, in which the three flange portions 25 e and 25 f of the brake-side side plate 25 are subjected to plastic deformation in such a manner that the distal end portions of the cylindrical portions 25 i and 25 j are increased in diameter outward.

Meanwhile, the operation lever 41 a made of, for example, a resin is coupled to the lever-side side plate 13 of the lever-side clutch portion 11, and the pinion gear 41 g meshing with the sector gear 41 f as a rotary member is provided to the output shaft 22 of the brake-side clutch portion 12. As illustrated in FIGS. 1, 13 a, 13 b, 14 a, and 14 b, the pinion gear 41 g is integrally formed at a distal end portion of the shaft portion 22 c of the output shaft 22.

In FIG. 39 b, when the operation lever 41 a is pivoted counterclockwise (upward), torque input in that direction is transmitted to the pinion gear 41 g through intermediation of the clutch unit X so that the pinion gear 41 g pivots counterclockwise. Then, the sector gear 41 f meshing with the pinion gear 41 g pivots clockwise so as to pull the other end of the link member 41 c through intermediation of the link member 41 e. As a result, the link member 41 c and the link member 41 d stand together, and a seat surface of the sitting seat 40 a becomes higher.

In this manner, when the operation lever 41 a is released after adjustment of the height H of the sitting seat 40 a, the operation lever 41 a pivots clockwise with the elastic force of the two centering springs 18 and 19, and returns to the original position (restores to the neutral state). Note that, when the operation lever 41 a is pivoted clockwise (downward), the seat surface of the sitting seat 40 a is lowered through operation in an opposite direction as that in the case described above. Further, when the operation lever 41 a is released after adjustment of the height, the operation lever 41 a pivots counterclockwise and returns to the original position (restores to the neutral state).

The present invention is not limited to the above-mentioned embodiments. As a matter of course, the present invention may be carried out in various modes without departing from the spirit of the present invention. The scope of the present invention is defined by claims, and includes the meaning of an equivalent of the claims and all the modifications within the claims. 

1-11. (canceled)
 12. A clutch unit, comprising: a lever-side clutch portion provided on an input side, for controlling transmission and interruption of rotational torque to an output side through lever operation; and a brake-side clutch portion provided on the output side, for transmitting torque input from the lever-side clutch portion to the output side and for interrupting torque reversely input from the output side, wherein the brake-side clutch portion comprises: an output-side member from which torque is output; a stationary-side member restricted in rotation; a plurality of pairs of engagement elements arranged in wedge gaps between the stationary-side member and the output-side member, for controlling transmission of the torque input from the lever-side clutch portion and interruption of the torque reversely input from the output side through engagement and disengagement between the stationary-side member and the output-side member; and an elastomer member inserted between the engagement elements of each pair, for imparting a repulsive force to the engagement elements of each pair.
 13. A clutch unit according to claim 12, wherein the elastomer member has an outside dimension larger than a gap between the engagement elements of each pair, and is inserted in an elastically deformed state between the engagement elements of each pair.
 14. A clutch unit according to claim 12, wherein the elastomer member has a columnar shape and has an axial dimension equal to or smaller than axial dimensions of the engagement elements of each pair.
 15. A clutch unit according to claim 12, wherein the elastomer member has a quadrangular prism shape and has an axial dimension equal to or smaller than axial dimensions of the engagement elements of each pair.
 16. A clutch unit according to claim 12, wherein the elastomer member is made of any one of a thermosetting elastomer and an elastically deformable resin material. 17-18. (canceled)
 19. A clutch unit according to claim 12, wherein the lever-side clutch portion and the brake-side clutch portion are incorporated in an automobile seat-lifter section.
 20. A clutch unit according to claim 13, wherein the elastomer member has a columnar shape and has an axial dimension equal to or smaller than axial dimensions of the engagement elements of each pair.
 21. A clutch unit according to claim 13, wherein the elastomer member has a quadrangular prism shape and has an axial dimension equal to or smaller than axial dimensions of the engagement elements of each pair.
 22. A clutch unit according to claim 13, wherein the elastomer member is made of any one of a thermosetting elastomer and an elastically deformable resin material.
 23. A clutch unit according to claim 14, wherein the elastomer member is made of any one of a thermosetting elastomer and an elastically deformable resin material.
 24. A clutch unit according to claim 15, wherein the elastomer member is made of any one of a thermosetting elastomer and an elastically deformable resin material.
 25. A clutch unit according to claim 20, wherein the elastomer member is made of any one of a thermosetting elastomer and an elastically deformable resin material.
 26. A clutch unit according to claim 21, wherein the elastomer member is made of any one of a thermosetting elastomer and an elastically deformable resin material. 